EP3864321A1 - Gearbox for vehicles and vehicles comprising such a gearbox - Google Patents
Gearbox for vehicles and vehicles comprising such a gearboxInfo
- Publication number
- EP3864321A1 EP3864321A1 EP19872186.2A EP19872186A EP3864321A1 EP 3864321 A1 EP3864321 A1 EP 3864321A1 EP 19872186 A EP19872186 A EP 19872186A EP 3864321 A1 EP3864321 A1 EP 3864321A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- gearbox
- coupling sleeve
- movable coupling
- axially movable
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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- 238000010168 coupling process Methods 0.000 claims abstract description 140
- 238000005859 coupling reaction Methods 0.000 claims abstract description 140
- 230000007935 neutral effect Effects 0.000 claims abstract description 36
- 239000003981 vehicle Substances 0.000 description 36
- 239000000306 component Substances 0.000 description 29
- 238000006073 displacement reaction Methods 0.000 description 9
- 238000002485 combustion reaction Methods 0.000 description 7
- 238000006243 chemical reaction Methods 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000008439 repair process Effects 0.000 description 3
- 239000000969 carrier Substances 0.000 description 2
- 229940000425 combination drug Drugs 0.000 description 2
- 238000004590 computer program Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
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- 238000010348 incorporation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000036647 reaction Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/70—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for change-speed gearing in group arrangement, i.e. with separate change-speed gear trains arranged in series, e.g. range or overdrive-type gearing arrangements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/10—Road Vehicles
- B60Y2200/14—Trucks; Load vehicles, Busses
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H2003/447—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the set of orbital gears and the output
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H2037/049—Forward-reverse units with forward and reverse gears for achieving multiple forward and reverse gears, e.g. for working machines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
Definitions
- Gearbox for vehicles and vehicles comprising such a gearbox.
- the invention relates to a gearbox for vehicles according to the appended claims.
- the invention also relates to a vehicle comprising such a gearbox according to the appended claims.
- a gearbox also called range gearbox
- Such an auxiliary gearbox usually includes a planetary gear, which has a low gear and a high gear, wherein the main gearbox shift facilities can be di vided into a low range gear position and a high range gear position. In the low range gear position a downshift takes place through the planetary gear, and in the high range gear the gear ratio is 1 :1 in the planetary gear.
- the range gearbox is usually provided between the main gearbox and a propeller shaft coupled to the drive wheels of the vehicle.
- the range gearbox is accommo dated in a gearbox housing and comprises an input shaft coupled to the main gear box, an output shaft and between the input shaft and the output shaft is the planetary gear disposed.
- the planetary gear usually comprises three components, which are rotatably arranged relative to each other namely a sun gear, a planet gear carrier with planet gears and a ring gear. With knowledge of the number of teeth of the sun gear and the ring gear the relative speed of the three components can be determined during operation.
- the sun gear can be rotatably connected to the input shaft, a number of planet gears which engage said sun gear, which planet gears are rotatably mounted on the planet gear carrier which is fixedly connected to the output shaft, and an axially displaceable ring gear which surrounds and engages the planet gears.
- the teeth of the sun gear, planet gears and ring gear can be heli cal, that is, they have an angle to a common rotation axis of the sun gear, planet gear carrier and ring gear.
- reaction force arises from the gears in the planetary gear in the direction of the rotation axis.
- the direction of the reaction force depends on the direction in which the gears of the planetary gear are helical.
- the reac tion force is directed backward or forward in the extension of the rotation axis.
- the low range gear position and high range gear position are obtained by displacing the ring gear axially between the low range gear position, in which the ring gear is rotationally locked relative to the gearbox housing, and high range gear position in which the ring gear is rotatably relative to the gearbox housing and where the ring gear, the planet gears and the sun gear rotate as a common unity.
- the planetary gear comprises two on each side of the ring gear arranged cou pling rings and two synchronizing rings arranged on each side of the ring gear. Syn- chronizer rings is to provide a synchronous shift.
- the document WO0155620 discloses a synchronization device in a planetary gear in which the planetary gear includes a sun gear, a planet gear carrier and a ring gear.
- the sun gear is rotatably connected with the input shaft and a number of planet gears engaging with the sun gear, which planet gears are rotatably mounted on the planet gear carrier, which is connected to the output shaft.
- An axially displaceable ring gear surrounds and meshes with the planet gears.
- Low and high gear are ob tained by the ring gear is displaced axially between low range gear and high range gear.
- the document US6196944 shows a planetary gear comprising a sun gear, a planet gear carrier with planet gears and a ring gear.
- the sun gear may be connected to the input shaft by means of a coupling sleeve in a low range gear position and disen gaged from the input shaft in a high range gear position.
- the input shaft is connected to of the planet gear carrier by means of the same coupling sleeve.
- the ring gear is firmly connected to a gearbox housing.
- the known planetary gear is arranged in an auxiliary gearbox, having only two gear positions.
- the reverse gear in a transmission in a vehicle are often arranged in the main gear box, which then comprises a gear which is engaged when the vehicle is to be driven in the reversed direction.
- the gear wheel, which is intended for the reverse gear causes an elongation of the main gearbox, and an undesired increase in weight of the vehicle.
- the reverse gear wheel rotates in the opposite direction to the other gears in the main gearbox, which causes losses.
- Said gear wheel which is intended for the reverse gear has a tendency to produce undesirable noise in the transmis sion, which is a result of an intermediate gear wheel disposed between a lay shaft and a main shaft in the main gearbox.
- the document US6196944 shows a gearbox for motor vehicles comprising a plane tary gear comprising a first and a second sleeve acting on the planet gear carrier, the ring gear, the gearbox housing and the output shaft.
- the first and second sleeves are controlled as one connected unit.
- An object of the present invention is therefore to provide a gearbox in which the time for shifting is short. Another object of the invention is to provide a gearbox in which the wear of the com ponents in the gearbox is low.
- a further object of the invention is to provide a gearbox in which the stress of the components in the gearbox is low.
- a gearbox for a vehicle comprising a planetary gear with a ring gear, a sun gear and a planet gear car rier, on which at least one planet gear is rotatably mounted, which ring gear and sun gear are configured to engage with the at least one planet gear; a gearbox housing surrounding the planetary gear; an input shaft and an output shaft for transfer of torque to and from the gearbox; a first axially movable coupling sleeve for selectively engaging and disengaging the planetary gear with/from the gearbox housing and for selectively engaging and disengaging the ring gear, the sun gear and the planet gear carrier with/from each other; and a second axially movable coupling sleeve for selec tively engaging and disengaging the output shaft with/from the ring gear and with/from the planet gear carrier; wherein the first axially movable coupling sleeve, in a first gear position, is configured to engage the first axially movable coupling sleeve,
- a vehicle wherein the vehi cle comprises such a gearbox.
- the time for shifting is short.
- the axial stroke of the respective cou pling sleeve is shorter compared with stroke length of the ring wheel of a traditional gearbox, which means that it is possible to quickly switch between different gear po sitions. Since the axial stroke of the coupling sleeves is short the velocity and the power needed for axially displacing the coupling sleeves will be low. The low axial velocity and the low power needed for displacing the couplings sleeves will reduce the force acting on the coupling sleeves, the planetary gear, the gearbox housing and on the output shaft at the moment of engagement. Axially directed end surfaces of these components, such as axially directed end surfaces of splines may resist wear and stress that may occur from these axial directed forces.
- the first coupling sleeve may be performed with a limited longitudinal extent, causing the weight of the coupling sleeve to be low.
- the low mass of the coupling sleeve means that it is pos sible to quickly shift between different gear positions.
- the low mass of the first coupling sleeve may reduce the power needed for axially displacing the first cou pling sleeve, which results in low wear and stress on the components for engage ment. Since the second axially movable coupling sleeve, in a neutral position, is con figured to be positioned in an intermediate axial position between the first and second gear positions an evenly wear on the engaging components is achieved.
- the second axially movable coupling sleeve When shift- ing the gearbox, the second axially movable coupling sleeve will first be moved into the neutral position and thereafter engage the ring gear or the output shaft, depend ing on the gear to be shifted. This will result in an evenly wear on the engaging com ponents, such as splines on the ring gear and on the planet gear carrier, which will be engaged by the second axially movable coupling sleeve.
- the vehicle comprising such a gearbox, has improved driving characteristics and an increased service of life.
- the reliability of the gearbox increases, also the reliability of the overall vehicle increases.
- Fig. 1 schematically illustrates a vehicle in a side view with a gearbox according to an embodiment
- Fig. 2 schematically illustrates a cross section of the gearbox according to an em bodiment in a low range gear position
- Fig. 3 schematically illustrates a cross section of the gearbox according to an em- bodiment in a neutral position
- Fig. 4 schematically illustrates a cross section of the gearbox according to an em bodiment in a high range gear position
- Fig. 5 schematically illustrates a cross section of the gearbox according to an em bodiment in a neutral position
- Fig. 6 schematically illustrates a cross section of the gearbox according to an em bodiment in a reverse position
- Fig. 7 schematically illustrates a cross section of the gearbox according to an em bodiment in a neutral position.
- the present disclosure relates to a gearbox for a vehicle.
- the axial stroke of coupling sleeves in the gearbox is short, which results in reduced velocity and power needed for axially displacing the coupling sleeves. This will reduce the force acting on com ponents in the gearbox, which will reduce wear and stress on these components.
- the gearbox according to the present disclosure is also so configured that an evenly wear on components, which engage and disengage each other, will occur.
- the present disclosure relates to a gearbox for a vehicle, the gearbox comprising a planetary gear with a ring gear, a sun gear and a planet gear carrier, on which at least one planet gear is rotatably mounted, which ring gear and sun gear are configured to engage with the at least one planet gear; a gearbox hous ing surrounding the planetary gear; an input shaft and an output shaft for transfer of torque to and from the gearbox; a first axially movable coupling sleeve for selectively engaging and disengaging the planetary gear with/from the gearbox housing and for selectively engaging and disengaging the ring gear, the sun gear and the planet gear carrier with/from each other; and a second axially movable coupling sleeve for selec tively engaging and disengaging the output shaft with/from the ring gear and with/from the planet gear carrier; wherein the first axially movable coupling sleeve, in a first gear position, is configured to engage
- the time for shifting is short. Since the axial stroke of the coupling sleeves is short the velocity and the power needed for axially displacing the coupling sleeves will be low. The low axial velocity and the low power needed for displacing the couplings sleeves will reduce the force acting on the coupling sleeves, the plane tary gear, the gearbox housing and on the output shaft at the moment of engage ment. Axially directed end surfaces of these components, such as axially directed end surfaces of splines may resist wear and stress that may occur from these axial directed forces. Further, the first coupling sleeve may be performed with a limited lon gitudinal extent, causing the weight of the coupling sleeve to be low.
- the low mass of the coupling sleeve means that it is possible to quickly shift between different gear positions.
- the low mass of the first coupling sleeve may reduce the power needed for axially displacing the first coupling sleeve, which results in low wear and stress on the components for engagement. Since the second axially movable cou pling sleeve, in a neutral position, is configured to be positioned in an intermediate axial position between the first and second gear positions an evenly wear on the en gaging components is achieved. When shifting the gearbox, the second axially mova ble coupling sleeve will first be moved into the neutral position and thereafter engage the ring gear or the output shaft, depending on the gear to be shifted.
- the first axially movable coupling sleeve is, in a third gear position, configured to connect the planet gear carrier with the gearbox housing
- the second axially movable coupling sleeve is, in the third gear position, configured to connect the ring gear with the output shaft.
- the third gear position corresponds to a reverse gear in the gearbox.
- a reverse gear in the gearbox is achieved when the first axially movable coupling sleeve is arranged to engage the planet gear carrier with the gearbox housing and the second axially movable coupling sleeve is arranged to engage the ring gear with the output shaft.
- Such a reverse gear results in an increased efficiency with lower losses.
- the reverse gear may easily be shifted by controlling the first and second axially displaceable coupling sleeves to the third gear position, corresponding to the reverse gear.
- the main shaft will exhibit less deflection when transmitting torque, which means that the life time of the bearings for the main shaft increases.
- the reverse gear is arranged in the range gearbox, the number of reverse gears in the transmission increases. The number of reverse gears may thus correspond with the number of gears in the main gearbox.
- the first axially movable coupling sleeve is, in the first gear position, configured to be disconnected from the sun gear and the planet gear carrier.
- the gear ratio through the planetary gear will in the first position be decided by the configuration of the sun gear and the planet gear carrier.
- the gearbox may be designed to fulfil the de mands of driveability of the vehicle.
- the sun gear and the planet gear carrier may be configured to satisfy demands on gear ratio in the gearbox in order to achieve the relevant downshift through the planetary gear in the first gear position.
- the first gear position may correspond to a low range position in a range gearbox.
- the first axially movable coupling sleeve is, in a fourth gear position, configured to disconnect the planetary gear from the gearbox housing and to disconnect the ring gear, the sun gear and the planet gear carrier from each other.
- a neutral position in the gearbox may be achieved by disengaging the planetary gear from the gearbox housing and to disconnect the ring gear, the sun gear and the planet gear carrier from each other.
- the gearbox In the neutral position the gearbox may transfer no torque.
- the input shaft of the gearbox may rotate without transfer torque and rotational speed to the output shaft of the gearbox.
- the neutral position in the gear box may be achieved by axially displacing the first axially movable coupling sleevein a fourth gear position, which is configured to disconnect the planetary gear from the gearbox housing and to disconnect the ring gear, the sun gear and the planet gear carrier from each other.
- Such neutral position controlled by the displacement of the first axially movable coupling sleeve, may be set in combination with a displacement of the second axially movable coupling sleeve to the neutral position.
- Such combina tion of neutral positions generated by both coupling sleeves may be used during ser- vice and repair of the gearbox.
- the synchronization when shifting gears in the gearbox may be more efficient if the second axially movable coupling sleeve en gages the output shaft and the planet gear carrier in the fourth gear position.
- the first axially movable coupling sleeve on an inner sur- face, comprises first splines, which are configured to engage with first splines ar ranged on the gearbox housing, the sun gear, the planet gear carrier and the ring gear.
- first splines A simple and efficient engagement and disengagement of the gearbox housing and the ring gear, the sun gear and the ring gear, and the gearbox housing and the planet gear carrier, respective, is achieved by means of the first splines.
- the axially directed end surfaces of splines may interfere with each other. This depends on how the components are di rected in the rotational direction in relation to each other.
- the second axially movable coupling sleeve on an inner surface, comprises second splines, which are configured to engage with second splines arranged on the ring gear, the planet gear carrier and the output shaft.
- a simple and efficient engagement and disengagement of the output shaft and the ring gear, and the output shaft and the planet gear carrier, respective, is achieved by means of the second splines.
- the axially directed end surfaces of splines may interfere with each other. This depends on how the components are directed in the rotational direction in relation to each other. Since the axial stroke of the second axially movable coupling sleeve is short the velocity and the power needed for axially displacing the second axially movable coupling sleeve will be low.
- the low axial velocity and the low power needed for displacing the second axially movable coupling sleeve will reduce the force acting on the second axially movable coupling sleeve, the planet gear carrier and the output shaft at the moment of engagement.
- wear and stress on the ax- ially directed end surfaces of the splines of these components may be reduced.
- the sun gear is connected to the input shaft of the gearbox. Torque from the input shaft is transferred directly to the sun gear. In the first gear po sition, corresponding to a low range position, the torque is transferred from the input shaft directly to the sun gear and further to the planetary wheels and the planet gear carrier to the output shaft. In the second gear position, corresponding to a high range position, the torque is transferred from the input shaft directly to the sun gear and fur ther to the ring gear and the output shaft.
- the gearbox is a range gearbox.
- a range gearbox aims to double the number of gear opportunities in a powertrain.
- the range gearbox may be shifted into two different gears.
- a downshift takes place through the range gearbox, and in a high range gear po sition, the gear ratio is 1 : 1 through the range gearbox.
- the input shaft is configured to be connected to a main gearbox.
- the range gearbox may be connected to a main gearbox in a powertrain.
- the number of gears in the main gearbox may be doubled by means of the range gear- box.
- the first gear position of the first and second axially mova ble coupling sleeves corresponds to a low range gear in the range gearbox.
- the planetary gear in the gearbox has a low and a high gear and shifting capability of the gearbox may therefore be divided into a low range gear and a high range gear.
- the first gear position corresponds to the low range gear position in the range gear box.
- a downshift takes place in the planetary gear when the range gearbox is shifted into the low range gear.
- the torque transferred through the range gearbox will increase when the range gearbox is shifted into the low range gear position.
- the second gear position of the first and second axially movable coupling sleeves corresponds to a high range gear in the range gearbox.
- the gear ratio is 1 :1 in the planetary gear.
- the present disclosure also relates to a vehicle, wherein the vehicle comprises a gearbox.
- Such vehicle may be a heavy vehicle, e.g. a truck or a bus.
- the vehicle may be man ually operated, remotely operated or autonomously operated.
- the vehicle may be propelled by an electrical engine and/or an internal combustion engine.
- Fig. 1 schematically illustrates a vehicle 1 in a side view with a gearbox 2 according to the present disclosure.
- the gearbox 2 is included in a powertrain 3, which com prises an internal combustion engine 4, a main gearbox 6 and a propeller shaft 10.
- the combustion engine 4 is coupled to the main gearbox 6, which in turn is con nected to the gearbox 2 of the present disclosure.
- the gearbox 2 is further connected to the drive wheels 8 of the vehicle 1 via the propeller shaft 10.
- the gearbox 2 of the present disclosure is a range gearbox, and aims to double the number of gear oppor tunities.
- the gearbox 2 is surrounded by a gearbox housing 12.
- Fig. 2 schematically illustrates a cross section of the gearbox 2 according to an em- bodiment in a low range gear position.
- the gearbox 2 comprises a planetary gear 14, which has a low and a high gear, so that the shifting capability of the main gearbox 6 can be divided into a low range gear position and a high range gear position.
- a downshift takes place in the planetary gear 14.
- the gear ratio is 1 :1 in the plan- etary gear 14.
- Fig. 2 shows the gearbox 2 in the first gear position, corresponding to the low range gear position.
- the gearbox 2 is accommodated in the gearbox housing 12 and comprises an input shaft 16 which may be a main shaft 26 of the main gearbox 6.
- the planetary gear 14 comprises three main components, which are rotatably arranged in relation to each other, namely a sun gear 18, a planet gear carrier 20 and a ring gear 22.
- a number of planet gears 24 are rotatably arranged with bearings on the planet gear carrier 20. With knowledge of the number of teeth 32 of sun gear 18 and the ring gear 22, the relative gear ratio of the three components can be determined.
- the sun gear 18 is ro tatably connected to the input shaft 16, so that torque and rotational movement may be transferred between the input shaft 16 and the sun gear 18.
- the planet gears 24 engage the sun gear 18.
- the ring gear 22 surrounds and engages the planet gears 24.
- the teeth 32 of the sun gear 18, the planet gears 24 and the ring gear 22 can be helical, so that they have an angle relative to a common axis of rotation 30 of the sun gear 18, the planet gear carrier 20 and the ring gear 22.
- a reaction force is obtained from the gears 18, 22, 24 in the planetary gear 14 in the direction of axis of rotation 30.
- the direction of the reaction force de pends on the direction in which the teeth 32 of the planetary gear 14 are bevelled
- the reaction force can be directed backward or forward in the axis of rotation 30.
- the input shaft 16 may connected to the sun gear 18 by means of a splines connec tion 34, which has an axial extent which allows an angular displacement between the input shaft 16 and the shaft 38 of the sun gear 18.
- a splines connec tion 34 which has an axial extent which allows an angular displacement between the input shaft 16 and the shaft 38 of the sun gear 18.
- main shaft 26 in the main gearbox 6 will under certain operating condition and great stress bend or curve due to its elasticity and resilient properties.
- a permissible angle displacement in the splines connection 34 results in that the sun gear 18 is not affected by bending of the main shaft 26, which reduces stresses on the sun gear 18 teeth 32.
- the splines connection 34 is preferably designed such that the planetary gear 14 can be assem bled and disassembled in one piece on the input shaft 16. Thus, the maintenance costs are reduced, since the time required for the repair decreases.
- a first axially displaceable coupling sleeve 42 is in a first gear position arranged to engage the gearbox housing 12 with the ring gear 22.
- the first axially movable cou- pling sleeve 42 is in the first gear position arranged to disengage the sun gear 18 from the ring wheel 22, and to disengage the planet gear carrier 20 from the gearbox housing 12.
- a second axially movable coupling sleeve 43 is configured for selectively engaging and disengaging the ring gear 22, planet gear carrier 20 and an output shaft 28 with/from each other.
- the second axially movable coupling sleeve 43 is in the first gear position configured to engage the planet gear carrier 20 with the output shaft 28,
- the first axially displaceable coupling sleeve 42 is on an inner surface provided with first splines 50 arranged to interact with the corresponding first splines 50 arranged on the ring gear 22 and on the periphery of a projection 52, which is fixedly con nected to the gearbox housing 12.
- the first splines 50 on the first axially displaceable coupling sleeve 42 are also arranged to cooperate with corresponding first splines 50 arranged on the input shaft 16.
- Corresponding first splines 50 disposed on the sun gear 18 are configured on the periphery of a first sprocket 46, which is mounted on the shaft 38 of the sun gear 18.
- the first sprocket 46 may be arranged on either side of the splines connection 34.
- the first splines 50 on the first axially displaceable coupling sleeve 42 are also ar ranged to cooperate with corresponding first splines 50 arranged on the planet gear carrier 20.
- Corresponding first splines 50 disposed on the planet gear carrier 20 are configured on the periphery of a second sprocket 44, which is mounted on the planet gear carrier 20.
- the number of first splines 50 of the first axially displaceable coupling sleeve 42 and input shaft 16 preferably may exceed the number of teeth 32 on the ring gear 22.
- a large number of discrete locked positions between the ring gear 22 and the first coupling sleeve 42 are obtained, which causes a large number of facets formed on teeth 32 of the gears 18, 22, 24.
- the facets are close together, so that they together will be experienced as an essentially smooth surface of the teeth 32. The facets therefore do not affect the gearbox 2 function and has no significant effect on the life-span of the gears 18, 22, 24.
- the second axially displaceable coupling sleeve 43 is on an inner surface provided with second splines 51 , which are arranged to cooperate with corresponding second splines 51 arranged on the ring gear 22, the planet gear carrier 20 and the output shaft 28.
- the corresponding second splines 51 arranged on the planet gear carrier 20 are configured on the periphery of a third sprocket 49, which is mounted on the planet gear carrier 20.
- the corresponding second splines 51 provided on the output shaft 28 are formed on the periphery of a fourth sprocket 53 which is mounted on the output shaft 28.
- An axial stop 54 arranged on the planet gear carrier 20 is adapted to abut against the ring gear 22, which axial stop 54 prevents the ring gear 22 to be moved axially.
- the axial stop 54 may comprise a disc-shaped plate, which by a first thrust bearing 56 is arranged on the planet gear carrier 20.
- the axial stop 54 is rotatably relative to the planet gear carrier 20 and the input shaft 16, and follows the rotation of the ring gear 22.
- the axial stop 54 fixates the ring gear 22 axially, and leads to that the axial bear ing of the input shaft 16 in the gearbox 2 is subjected to less stress when the gears 18, 22, 24 are provided with helical teeth.
- the low gear in the gearbox 2 is obtained by displacing the second coupling sleeve 42, so that the ring gear 22 is connected to the gearbox housing 12.
- the axial dis placement of the first and second coupling sleeves 42, 43 are provided with a first and second shift fork 60, 61 arranged in an outside circumferential groove 62 in the respective coupling sleeve 42, 43.
- the first shift fork 60 is influenced by a first power means 66 and the second shift fork 61 is influenced by a second power means 67.
- the first and second power means 66, 67 may be a pneumatic or hydraulic cylinder.
- the shift forks 60, 61 and power means 66, 67 are schematically illustrated in Fig. 2.
- the axial stroke of the coupling sleeves 42, 43 is short and the velocity and the power needed for axially displacing the coupling sleeves 42, 43 will be low.
- the low axial velocity and the low power needed for displacing the couplings sleeves 42, 43 will reduce the force acting on the coupling sleeves 42, 43, the components 18, 20,
- first axially mova ble coupling sleeve 42 may be performed with a limited longitudinal extent, causing the weight of the first axially movable coupling sleeve 42 to be low.
- the low mass of the first axially movable coupling sleeve 42 means that it is possible to quickly shift between different gear positions.
- the low mass of the first axially movable coupling sleeve 42 may reduce the power needed for axially displacing the first axi ally movable coupling sleeve 42, which results in low wear and stress on the compo nents for engagement.
- Fig. 3 schematically illustrates a cross section of the gearbox 2 according to an em bodiment in a neutral position.
- the second axially movable coupling sleeve 43 has been displaced and disengaged from the planetary gear car rier 20 to a position where the second axially movable coupling sleeve 43 only is con- nected to output shaft 28.
- the ring gear 22 is free to ro tate in relation to the output shaft 28.
- the gearbox 2 will not transfer any torque from the input shaft 16 to the output shaft 28.
- the second axially movable coupling sleeve 43 is in a neutral position configured to be positioned in an intermediate axial position between the ring gear 22 and the planet gear carrier 20.
- the second splines 51 on the second axially movable coupling sleeve 43 still engages the second splines 51 on the output shaft 28, but has disen gaged the second splines 51 on the ring gear 22 and on the planet gear carrier 20.
- the neutral may be reached by arranging the second splines 51 of the ring gear 22 and the second splines 50 of the planet gear carrier 20 at an axially distance to each other.
- This distance between the ring gear 22 and the planet gear carrier 20 allows the second splines 51 of the second axially movable coupling sleeve 43 to be disen gaged from both the ring gear 22 and the planet gear carrier 20.
- the second axially movable coupling sleeve 43 will first be moved into the neutral posi tion. After gear shifting is accomplished, the planet gear carrier 20 and the output shaft 28 are engaged, if the gear in question is a low range gear. In Fig. 3 the first ax ially movable coupling sleeve 42 still is in the first position and thus still engages the ring gear 22 and the gearbox housing 12. This will result in an evenly wear on the second splines 51 on the ring gear 22 and on the output shaft 28.
- Fig. 4 schematically illustrates sectional view of the gearbox 2 according to the dis closure in the second gear position or high range gear position.
- the first axially movable coupling sleeve 42 engages the sun gear 18 and the ring gear 22.
- the second axially movable coupling sleeve 43 engages the ring gear 22 and the output shaft 28.
- Torque from the input shaft 16 to the output shaft 28 is in the high range gear position transferred from the input shaft 16 and sun gear to the ring gear 22 and further to the output shaft. This results in that the gear ratio through the planetary gear 14 becomes 1 :1.
- Fig. 5 schematically illustrates a cross section of the gearbox according to an em bodiment in a neutral position.
- the second axially movable coupling sleeve 43 will first be dis placed to the neutral position.
- the ring gear 22 and the output shaft 28 are engaged, if the gear in question is a high range gear.
- the first axially movable coupling sleeve 42 still is in the second position and thus still engages the ring gear 22 and the sun gear 18.
- the next coming gear position may be reached from the neutral position in two different ways. If the following gear is a low range gear, the second axially movable coupling sleeve 43 will be shifted from the neutral position to the first gear position in which the second axially movable coupling sleeve 43 en- gages the planet gear carrier 20 and the output shaft 28. If the following gear is a high range gear, the second axially movable coupling sleeve 43 will be shifted from the neutral position to the second gear position in which the second axially movable coupling sleeve 43 engages the ring gear 22 and the output shaft 28. Thus, second axially movable coupling sleeve 43 may alternately engage the planet gear carrier 20 and the ring gear 22. This will result in an evenly wear on the second splines 51 on the ring gear 22 and on the output shaft 28.
- the gearbox 2 functions as follows when shifting from the first to the second gear position, that is, from the low range gear position to the high range gear position and to be described in connection with Figures 2 - 5.
- the gearbox 2 has been shifted into the low range gear position, which means that the first axially movable coupling sleeve 42 has been shifted to a position to connect the ring gear 22 with the gearbox housing 12.
- a downshift takes place through the planetary gear 14.
- the shift ing operation from the low range gear position to the high range gear position is made by disengaging the planet gear carrier 20 from the output shaft 28 by means of the second axially movable coupling sleeve 43.
- This disengagement may be possible when no torque transferred between the planet gear carrier 20 from the output shaft 28, which may be accomplished by disconnecting the internal combustion engine 4 from the main gear box 6 through disconnection of a clutch 68.
- the in ternal combustion engine 4 is controlled to generate a torque balance between the planet gear carrier 20 from the output shaft 28.
- the second axially movable coupling sleeve 43 no longer transfer any torque the axial displacement of the sec ond axially movable coupling sleeve 43 is possible.
- the first axially movable coupling sleeve 42 may after synchronization be displaced in order to engage the sun gear 18 with the ring gear 22.
- the rotational speed of the ring gear 22 is synchronized with the rotational speed of the output shaft 28, so that the second axially movable coupling sleeve 43 may engage the ring gear 22 with the output shaft 28.
- the gearbox 2 operates in the high range gear position.
- Fig. 6 schematically illustrates a cross section of the gearbox 2 according to an em- bodiment in a reverse position.
- the gearbox 2 has been shifted into the third gear position, which is the reverse gear.
- the second axially displaceable sleeve 43 is in the third gear position arranged to connect the ring gear 22 with output shaft 28.
- the second coupling sleeve 43 is shifted by the second shift fork 61 , so that the ring gear 22 is connected to the output shaft 28 and the ring gear 22.
- the first cou- pling sleeve 42 is shifted by the first shift fork 60 to couple the planet gear carrier 20 with the gearbox housing 12.
- the displacement of the respective clutch sleeve 42, 43 is performed when the input and the output shaft 16, 28 are stationary, which corre sponds to a stationary operating state of the vehicle 1 , when the gearbox 2 is in cluded in the powertrain 3 of the vehicle 1.
- the clutch 68 of the vehicle 1 is transferred to a disconnected mode.
- torque is transmit ted from the input shaft 16 to the sun gear 18 and further to the planet gears 24 which transmits the torque to the ring gear 22 and further to the output shaft 28 via the second coupling sleeve 43.
- the planet gear carrier 20 is stationary as the first coupling sleeve 42 connects the planet gear carrier 20 with the gearbox housing 12.
- Fig. 7 schematically illustrates a cross section of the gearbox according to an em- bodiment in a neutral position.
- the first axially movable coupling sleeve 42 may in a fourth gear position be configured to disengage the planetary gear 14 from the gear box housing 12 and to disengage the ring gear 22, the sun gear 18 and the planet gear carrier 28 from each other.
- a neutral position may thus be achieved in the gear box 2.
- the gearbox In the neutral position the gearbox may transfer no torque.
- the input shaft of the gearbox may rotate without transferring torque and rotational speed to the output shaft of the gearbox.
- the neutral may be reached by arranging the first splines 50 of the gearbox housing 12 and the first splines 50 of the sun gear 18 at an axially distance to each other.
- This distance between the gearbox housing 12 and the sun gear 18 allows first splines of the first axially movable coupling sleeve 42 to be disengaged from both the gearbox housing 12 and the sun gear 18.
- the neutral posi tion according to fourth gear position controlled by the displacement of the first axi ally movable coupling sleeve 42, may be set in combination with a displacement of the second axially movable coupling sleeve 43 to the neutral position.
- Such combina tion of neutral positions generated by both coupling sleeves 42, 43 may be used dur- ing service and repair of the gearbox 2.
- the first coupling sleeve 42 may provided with three circular areas. Two areas are contact areas and are provided with the first splines 50. Between the two contact ar eas a central area is provided which separates the two contact areas from each other.
- the second coupling sleeve 43 may also be provided with three circular areas. Two areas are contact areas and are provided with the second splines 51. Between the two contact areas a central area is provided which separates the two contact ar eas from each other.
- An electronic control device 70 is coupled to the gearbox 2, the main gearbox 6, the combustion engine 4 and the clutch 68 to achieve the gear shifting above.
- a number of not shown speed sensors in the gearbox 2, in the main gear box 6 and in the internal combustion engine 4 may be connected to the control device 70.
- An other computer 72 may also be connected to the control device 70.
- the control de vice 70 may be a computer with appropriate software for this purpose.
- the control device 70 and/or the computer 72 comprise a computer program P, which can in clude routines to control the gearbox 2 of the present disclosure.
- the program P may be stored in an executable form or compressed form in a memory M and/or in a read/write memory.
- a computer program product com prising a program code stored on a, by a computer readable medium for performing the gear shiftings above, when said program is run on the control device 70 or an other computer 72 connected to the control device 70.
- Said code may be non-vola tile, stored in said computer readable medium.
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Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE1851227A SE542585C2 (en) | 2018-10-09 | 2018-10-09 | Range gearbox for vehicles and vehicles comprising such a gearbox |
PCT/SE2019/050858 WO2020076206A1 (en) | 2018-10-09 | 2019-09-12 | Gearbox for vehicles and vehicles comprising such a gearbox |
Publications (3)
Publication Number | Publication Date |
---|---|
EP3864321A1 true EP3864321A1 (en) | 2021-08-18 |
EP3864321A4 EP3864321A4 (en) | 2022-06-22 |
EP3864321B1 EP3864321B1 (en) | 2023-12-06 |
Family
ID=70163844
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19872186.2A Active EP3864321B1 (en) | 2018-10-09 | 2019-09-12 | Gearbox for vehicles and vehicles comprising such a gearbox |
Country Status (6)
Country | Link |
---|---|
US (1) | US11280392B2 (en) |
EP (1) | EP3864321B1 (en) |
CN (1) | CN112771287B (en) |
RU (1) | RU2762578C1 (en) |
SE (1) | SE542585C2 (en) |
WO (1) | WO2020076206A1 (en) |
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2018
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-
2019
- 2019-09-12 US US17/277,757 patent/US11280392B2/en active Active
- 2019-09-12 CN CN201980065160.5A patent/CN112771287B/en active Active
- 2019-09-12 WO PCT/SE2019/050858 patent/WO2020076206A1/en active Application Filing
- 2019-09-12 EP EP19872186.2A patent/EP3864321B1/en active Active
- 2019-09-12 RU RU2021112269A patent/RU2762578C1/en active
Also Published As
Publication number | Publication date |
---|---|
EP3864321A4 (en) | 2022-06-22 |
CN112771287B (en) | 2024-06-18 |
SE542585C2 (en) | 2020-06-09 |
BR112021005754A2 (en) | 2021-06-22 |
EP3864321B1 (en) | 2023-12-06 |
SE1851227A1 (en) | 2020-04-10 |
US11280392B2 (en) | 2022-03-22 |
CN112771287A (en) | 2021-05-07 |
US20210356023A1 (en) | 2021-11-18 |
RU2762578C1 (en) | 2021-12-21 |
WO2020076206A1 (en) | 2020-04-16 |
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